US6877928B2 - Construction of coupling spline sections of automatic transmission - Google Patents

Construction of coupling spline sections of automatic transmission Download PDF

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Publication number
US6877928B2
US6877928B2 US10/251,844 US25184402A US6877928B2 US 6877928 B2 US6877928 B2 US 6877928B2 US 25184402 A US25184402 A US 25184402A US 6877928 B2 US6877928 B2 US 6877928B2
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United States
Prior art keywords
section
spline
end side
rotary
shaft
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Expired - Lifetime, expires
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US10/251,844
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English (en)
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US20030061892A1 (en
Inventor
Yasuaki Yumoto
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JATCO Ltd
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JATCO Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/0018—Shaft assemblies for gearings
    • F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7026—Longitudinally splined or fluted rod
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T403/00—Joints and connections
    • Y10T403/70—Interfitted members
    • Y10T403/7026—Longitudinally splined or fluted rod
    • Y10T403/7035—Specific angle or shape of rib, key, groove, or shoulder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19633—Yieldability in gear trains
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/1966—Intersecting axes
    • Y10T74/19665—Bevel gear type

Definitions

  • the present invention relates to a construction of coupling spline sections of an automatic transmission.
  • An automatic transmission constituting three axles has a mission case including an input shaft, a counter shaft, a drive shaft which are arranged in parallel. On the above shafts, there are arranged various elements such as a transmission unit, a gear and the like.
  • a counter driven gear 302 which is coaxially coupled with a counter shaft 300 , wherein the counter shaft 300 is disposed between an input shaft and a dive shaft while the counter driven gear 302 meshes with a counter drive gear 301 disposed on the input shaft's side.
  • the counter shaft 300 has a first end side (left in FIG. 5 ) which is formed with a small-diameter shaft section 304 , and a second end side (right in FIG. 5 ) which is formed with a reduction gear 306 united with the small-diameter shaft section 304 .
  • the small-diameter shaft section 304 has an outer periphery which is formed with a spline section 308 .
  • a tubular section 310 which is united with the counter driven gear 302 .
  • the tubular section 310 has an inner periphery which is formed with a spline section 312 .
  • the spline section 312 of the tubular section 310 can be coupled with the spline section 308 of the small-diameter shaft section 304 .
  • a nut 314 is screwed down on a first end (left in FIG. 5 ) of the small-diameter shaft section 304 , in such a manner as to press the tubular section 310 on the reduction gear 306 's side. This can constrain an axial movement of the counter driven gear 302 .
  • the counter shaft 300 can be rotatably born by means of the radial bearing 318 .
  • the spline section 308 of the small-diameter shaft section 304 can be coupled, in an entire axial range thereof, with the spline section 312 of the tubular section 310 in a press fitting state.
  • Too great a press fitting force may expand the tubular section 310 , thereby applying a stress to the radial bearing 318 from inside. Too great a stress may reduce accuracy of the radial bearing 318 in rotatably bearing the counter shaft 300 , to thereby deteriorate durability.
  • the tubular section 310 is to be designed thick. This may involve a large size of the whole unit.
  • a construction of coupling spline sections of an automatic transmission comprises: a rotary shaft section having an outer periphery formed with a spline section; a rotary hollow section having an inner periphery formed with a spline section which is coupled with the spline section of the rotary shaft section in a press fitting state; a support member; and a bearing disposed between a part of an outer periphery of the rotary hollow section and the support member.
  • the bearing rotatably bears the rotary shaft section in such a manner as to transmit a torque between the rotary shaft section and the rotary hollow section.
  • the spline section of the rotary shaft section and the spline section of the rotary hollow section which are disposed at least inside the bearing are coupled with each other in a loose state looser than the press fitting state.
  • FIG. 1 is a skeleton diagram of a construction of an automatic transmission, according to an embodiment of the present invention.
  • FIG. 2 is a table showing operations of the automatic transmission.
  • FIG. 3 shows a construction around a counter gear 400 , according to the embodiment of the present invention.
  • FIG. 4 is an enlarged view of essential portions, according to the embodiment of the present invention.
  • FIG. 5 shows a construction around a counter gear, according to a related art.
  • FIG. 1 there is provided a gear train (skeleton diagram) of an automatic transmission, according to an embodiment of the present invention.
  • the automatic transmission shown in FIG. 1 is what is called a 3-axle transmission, namely, a transaxle which is disposed laterally in an FF (front engine and front drive) vehicle and/or an RR (rear engine and rear drive) vehicle. Moreover, the transmission gear is provided with a gear train achieving six forward speeds and one reverse speed.
  • the automatic transmission has a mission case 180 which is constituted of an input shaft 50 (primary shaft), a counter shaft 401 , a differential shaft 453 a , a differential shaft 453 b and the like arranged in parallel with each other. Moreover, various elements such as a transmission unit, a gear and the like are disposed on each of the above shafts.
  • a torque is inputted into the input shaft 50 from an engine (not shown in FIG. 1 , but assumes right in FIG. 1 ) by way of a torque converter.
  • the input shaft 50 has an output side which is disposed on the torque converter's side.
  • the counter shaft 401 is disposed in parallel with the input shaft 50 .
  • the counter shaft 401 has a counter gear 400 which meshes with an output gear of the input shaft 50 .
  • a differential carrier 451 carrying the differential shaft 453 a and the differential shaft 453 b is provided with a final gear 452 to which the torque is transmitted by way of the counter gear 400 of the counter shaft 401 .
  • the differential shaft 453 a is a left shaft which makes a deferential revolution due to a differential gear
  • the differential shaft 453 b is a right shaft which makes the differential revolution due to the differential gear.
  • the automatic transmission is provided with the transmission unit around the input shaft 50 .
  • the transmission unit is constituted of a first planetary gear set 10 , a second planetary gear set 30 , a first clutch 60 , a third clutch 80 , a second clutch 70 , a first brake 100 , a second brake 110 , and a one-way clutch 90 .
  • the first planetary gear set 10 can output a plurality of transmission speeds from an input speed, namely, a reduction speed and a non-reduction speed of the input shaft 50 .
  • the second planetary gear set 30 can output the reduced speed of the input shaft 50 .
  • the second planetary gear set 30 and the first planetary gear set 10 have, respectively, a large-diameter sun gear 11 and a small-diameter sun gear 12 having diameters different from each other.
  • the first clutch 60 and the third clutch 80 are engageably and disengageably interposed between the large-diameter sun gear 11 and the small-diameter sun gear 12 .
  • the second clutch 70 is engageably and disengageably interposed between the input shaft 50 and a second carrier 14 of the first planetary gear set 10 .
  • the first brake 100 can brake the large-diameter sun gear 11 of the first planetary gear set 10
  • the second brake 110 can brake the first carrier 13 of the first planetary gear set 10 .
  • the one-way clutch 90 is interposed in parallel with the second brake 110 .
  • Each of the first clutch 60 , the second clutch 70 , the first clutch 80 , the first brake 100 , and the second brake 110 is a frictional member, and in a form of a multiple-disk.
  • the first clutch 60 is disposed in the vicinity of an outer periphery of the second planetary gear set 30 .
  • the third clutch 80 is disposed backward the first clutch 60 .
  • the second clutch 70 is disposed at a front end of the mission case 180 .
  • the first brake 100 is disposed between the first clutch 60 and an inner periphery of the mission case 180 .
  • the second brake 110 is disposed between the first planetary gear set 10 and the inner periphery of the mission case 180 .
  • the one-way clutch 90 is disposed between the first brake 100 and the second brake 110 .
  • the first planetary gear set 10 is constituted of the following four transmission elements: 1) the large-diameter sun gear 11 , 2) the small-diameter sun gear 12 , 3) the first carrier 13 and the second carrier 14 , and 4) the ring gear 17 .
  • a long pinion 15 can mesh with the large-diameter sun gear 11
  • a short pinion 16 can mesh with the small-diameter sun gear 12 .
  • the long pinion 15 can mesh with inner teeth of the ring gear 17 , constituting a ravigneaux gear.
  • the large-diameter sun gear 11 and the small-diameter sun gear 12 constitute the input element for reduced speed, where the input from the input shaft 50 is transmitted by way of the second planetary gear set 30 .
  • the small-diameter sun gear 12 connects to the first clutch 60 , thus receiving the input from the second planetary gear set 30 .
  • the large-diameter sun gear 11 connects to the third clutch 80 , thus receiving the input from the second planetary gear set 30 . Moreover, the large-diameter sun gear 11 can be fixed to the mission case 180 by means of the first brake 100 .
  • the first carrier 13 and the second carrier 14 can carry the long pinion 15 and the short pinion 16 meshing with each other.
  • the first carrier 13 and the second carrier 14 constitute the input element of a non-reduction speed, wherein the input speed is directly transmitted from the input shaft 50 .
  • the second carrier 14 connects to the input shaft 50 by way of the second clutch 70 .
  • the first carrier 13 can be fixed to the mission case 180 by means of the second brake 110 .
  • the one-way clutch 90 allows one-way speed only relative to the mission case 180 .
  • the one-way clutch 90 defines an engagement direction which direction is the same as that of the reverse torque at the first speed, thereby effecting the second brake 110 .
  • the ring gear 17 constitutes an output element, and connects to a counter drive gear 170 .
  • the counter drive gear 170 is disposed between the first planetary gear set 10 and the second clutch 70 . As described hereinafter, the counter drive gear 170 is rotatably supported to a middle bulkhead 195 which is separated from
  • the second planetary gear set 30 is constituted of the following three transmission elements: a sun gear 31 , a ring gear 32 , and a carrier 33 .
  • the sun gear 31 is fixed to a sleeve member 210 which is formed on a side cover 200 of the mission case 180 , to be described afterward.
  • the ring gear 32 connects to the input shaft 50 .
  • the carrier 33 connects to the first planetary gear set 10 by way of the first clutch 60 and the second clutch 80 .
  • the counter gear 400 is constituted of a counter driven gear 402 and a reduction gear 403 .
  • the counter driven gear 402 having a large diameter can mesh with the counter drive gear 170 fixed on the back end side of the counter shaft 401 which is in parallel with the input shaft 50 and shorter than the input shaft 50 .
  • the reduction gear 403 having a small diameter is the output element.
  • the reduction gear 403 is fixed on the front end side relative to the counter driven gear 402 .
  • the counter gear 400 can reduce and reverse the output speed from the input shaft 50 , and send the output speed (reduced and reversed) to a differential device 450 , thereby effecting a proper reduction ratio.
  • the differential device 450 allows a differential gear 452 fixed in a deferential case (not shown) to mesh with the reduction gear 403 of the counter gear 400 . With this, a differential speed of the differential gear disposed in the differential case (not shown) can be outputted to the differential shaft 453 a and the differential shaft 453 b.
  • the automatic transmission having the construction described above can effect transmission by means of an electronic controller (not shown) and a hydraulic controller (not shown), based on vehicular load and in a transmission range selected by a driver.
  • the above transmission include six forward speeds (1ST to 6TH) and one reverse speed (REV).
  • FIG. 2 shows tabulated transmission steps effected by engagement and disengagement of each of the clutches and the brakes, wherein “E” denotes engagement while “blank” denotes disengagement.
  • the first speed (1ST) may be effected by engagement of the first clutch 60 and engagement of the second brake 110 . Effecting the first speed (1ST) may take the following operations:
  • the second speed (2ND) may be effected by engagement of the first clutch 60 and engagement of the first brake 100 . Effecting the second speed (2ND) may take the following operations:
  • the third speed (3RD) may be effected by synchronous engagements, namely engagement of the first clutch 60 and engagement of the third clutch 80 . Effecting the third speed (3RD) may take the following operations:
  • the fourth speed (4TH) may be effected by synchronous engagements, namely engagement of the first clutch 60 and engagement of the second clutch 70 . Effecting the fourth speed (4TH) may take the following operations:
  • the fifth speed (5TH) may be effected by synchronous engagements, namely engagement of the second clutch 70 and engagement of the third clutch 80 . Effecting the fifth speed (5TH) may take the following operations:
  • the sixth speed (6TH) may be effected by engagement of the second clutch 70 and engagement of the first brake 100 . Effecting the sixth speed (6TH) may take the following operations:
  • the reversed speed (REV) may be effected by engagement of the third clutch 80 and engagement of the second brake 110 . Effecting the reversed speed (REV) may take the following operations:
  • FIG. 3 shows a detailed construction of the counter gear 400 described above.
  • the counter gear 400 is constituted of the counter driven gear 402 and the reduction gear 403 .
  • the counter driven gear 402 connects to the small-diameter shaft section 410 which is disposed on the first end side (left in FIG. 3 ) of the counter shaft 401 , while the reduction gear 403 is unitedly formed on the second end side (right in FIG. 3 ) of the counter shaft 401 .
  • the counter driven gear 402 is equipped with a tubular section 412 having an inner periphery which is formed with a spline section 414 .
  • the small-diameter shaft section 410 has an outer periphery which is formed with a spline section 416 . Fitting the tubular section 412 over the small-diameter shaft section 410 can allow the spline section 414 and the spline section 416 to mate with each other, causing a spline coupling.
  • the tubular section 412 is formed with substantially a tubular or cylindrical portion 412 a and an extended portion 412 b which extends substantially orthogonally relative to the cylindrical portion 412 a .
  • the counter shaft 401 can be rotatably born by a first radial bearing 426 and a second radial bearing 428 .
  • first radial bearing 426 is disposed between an inner wall of the mission case 180 and an outer periphery of the tubular section 412
  • second radial bearing 428 is disposed between the inner wall of the mission case 180 and an outer periphery ⁇ on the second end side (right in FIG. 3 ) ⁇ of the counter shaft 401 .
  • the first radial bearing 426 is constituted of an outer race 426 a abutting on the inner wall of the mission case 180 , an inner race 426 b abutting on the outer periphery of the tubular section 412 , and a tube 426 c rollably disposed between the outer race 426 a and the inner race 426 b
  • the second radial bearing 428 is constituted of an outer race 428 a abutting on the inner wall of the mission case 180 , an inner race 428 b abutting on the outer periphery ⁇ on the second end side (right in FIG.
  • first thrust bearing 430 between the outer race 426 a (of the first radial bearing 426 ) and a side face (left in FIG. 3 ) of the counter driven gear 402
  • second thrust bearing 432 between the outer race 428 a (of the second radial bearing 428 ) and a side face (right in FIG. 3 ) of the reduction gear 403 .
  • the spline section 416 disposed on the outer periphery of the small-diameter shaft section 410 has concave rows and convex rows which are alternately arranged circumferentially.
  • a convex row 416 a on the first end side defines a first external diameter dimension D 1
  • the convex row 416 a is disposed inside the first radial bearing 426 .
  • a convex row 416 b on the second end side defines a second external diameter dimension D 2 .
  • the first external diameter dimension D 1 is set smaller than the second external diameter dimension D 2 (D 1 ⁇ D 2 ).
  • the spline section 416 on the first end side (left in FIG. 4 ) formed with the convex row 416 a (defining the first external diameter dimension D 1 [small]) can be coupled with the spline section 414 of the tubular section 412 in such a manner as to cause a loose spline-coupling state
  • the spline section 416 on the second end side (right in FIG. 4 ) formed with the convex row 416 b (defining the second external diameter dimension D 2 [large]) can be coupled with the spline section 414 of the tubular section 412 in such a manner as to cause a press fitting state.
  • the first radial bearing 426 disposed on the outer periphery of the small-diameter shaft section 410 can be free from any stress which may direct from radially inside to radially outward.
  • the counter shaft 401 can be rotatably born in an ordinary state.
  • the inner periphery of the tubular section 412 can be free from any crack, split and the like, since no stress attributable to expansion of the small-diameter shaft section 410 is applied to the inner periphery on the first end side (left in FIG. 4 ) of the tubular section 412 .
  • the convex row 416 a on the first end side can act as guide for causing the spline coupling of the spline section 414 (of the tubular section 412 ) with the spline section 416 (of the counter shaft 401 ).
  • the counter driven gear 402 can be mounted to the small-diameter shaft section 410 with ease.
  • the area covered by the second external diameter dimension D 2 of the convex row 416 b of the spline section 416 is press fitted to the spline section 414 .
  • the present invention is, however, not limited to this.
  • the following construction of the convex row 416 a and the convex row 416 b is allowed:
  • the external diameter dimensions are differentiated between the following two convex rows, namely, the convex row 416 a (disposed inside the first radial bearing 426 ) of the spline section 416 disposed on the outer periphery of the small-diameter shaft section 410 , and the convex row 416 b on the second end side (right in FIG. 4 ).
  • the present invention is, however, not limited to this.
  • a reversed construction is allowed, in other words, the spline section 414 of the tubular section 412 can be replaced with the spline section 416 of the small-diameter shaft section 410 . More specifically described as follows:
  • the automatic transmission has the gear train effecting six forward speeds.
  • the present invention is, however, not limited this. More specifically, gear trains of the automatic transmission effecting five or less forward speeds, or seven or more forward speeds can be allowed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Structure Of Transmissions (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Gears, Cams (AREA)
US10/251,844 2001-09-28 2002-09-23 Construction of coupling spline sections of automatic transmission Expired - Lifetime US6877928B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001303914A JP2003106339A (ja) 2001-09-28 2001-09-28 自動変速機におけるスプライン部の結合構造
JP2001-303914 2001-09-28

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US20030061892A1 US20030061892A1 (en) 2003-04-03
US6877928B2 true US6877928B2 (en) 2005-04-12

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EP (1) EP1298354B1 (ja)
JP (1) JP2003106339A (ja)
DE (1) DE60228917D1 (ja)

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US20140162834A1 (en) * 2011-07-25 2014-06-12 Zf Friedrichshafen Ag Gearwheel, in particular planet gear for a planetary gear set, and rotary vibration damping arrangement having a gearwheel of said type
DE102015215117A1 (de) 2015-08-07 2017-02-09 Schaeffler Technologies AG & Co. KG Vorrichtung zur radialen Lagerung sowie axialen Abstützung eines Mehrfachzahnrads

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KR100598874B1 (ko) * 2003-11-17 2006-07-10 현대자동차주식회사 자동변속기
GB2427254A (en) * 2005-06-15 2006-12-20 Cnh Belgium Nv Final drive for an agricultural vehicle
JP4743890B2 (ja) * 2007-01-12 2011-08-10 Ｎｔｎ株式会社 車輪用軸受装置
JP2009216176A (ja) * 2008-03-10 2009-09-24 Sumitomo Metal Ind Ltd やまば歯車及びその組立方法並びに鉄道車両用歯車装置
JP2016102569A (ja) * 2014-11-28 2016-06-02 アイシン・エーアイ株式会社 変速機
DE102014225439A1 (de) * 2014-12-10 2016-06-16 Zf Friedrichshafen Ag Stufenplanet
JP6430242B2 (ja) * 2014-12-26 2018-11-28 オリエンタルモーター株式会社 歯車構造体
JP6187453B2 (ja) * 2014-12-26 2017-08-30 株式会社豊田自動織機 減速機
JP6673093B2 (ja) * 2016-08-12 2020-03-25 株式会社豊田自動織機 ギア構造及びギアの製造方法
ES2781191T3 (es) 2017-06-26 2020-08-31 Flender Gmbh Engranaje

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JP2003106339A (ja) 2003-04-09
US20030061892A1 (en) 2003-04-03
EP1298354B1 (en) 2008-09-17

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